DE102017206803A1 - Transmission for a motor vehicle - Google Patents

Abstract

The invention relates to a transmission (G) for a motor vehicle, wherein the transmission (G) a transmission input (GW1-A), a transmission output (GW2-A), five planetary gear sets (P1, P2, P3, P4, P5) and six switching elements (B1, B2, K1, K2, K3, B3), wherein by selectively operating the six switching elements (B1, B2, K1, K2, K3, B3) ten forward gears and two reverse gears between the transmission input (GW1-A) and Transmission output (GW2-A) are switchable, and powertrain for a motor vehicle with such a transmission (G).

Description

The invention relates to a transmission for a motor vehicle, comprising a transmission input and a transmission output, and a first, a second, a third, a fourth and a fifth planetary gear, wherein the planetary gear sets each comprise a plurality of elements, wherein a first, a second, a third , a fourth, a fifth and a sixth switching element are provided, through the selective actuation of different power flow guides on the planetary gear trains under different gears between transmission input and transmission output can be displayed.

In the present case, a transmission is thus a multi-speed transmission, d. H. There are several different ratios as gears between the transmission input and the transmission output of the transmission can be switched by operating corresponding switching elements, and this is preferably done automatically. Depending on the arrangement of the switching elements, these are clutches or brakes. Such transmissions are mainly used in motor vehicles to implement a traction power supply of a prime mover of the respective motor vehicle in terms of various criteria suitable.

From the KR 20160072696 A goes out a gearbox comprising five planetary gear sets, each composed of several elements in the form of one sun gear, one planetary land and one ring gear each. In addition, six switching elements are provided, through whose selective actuation different gears between a transmission input and a transmission output of the transmission can be represented. Overall, ten forward gears, as well as a reverse gear between the transmission input and the transmission output can be switched.

It is the object of the present invention to provide an alternative embodiment to the prior art transmission with ten forward gears and one reverse between a transmission input and a transmission output.

This object is achieved on the basis of the preamble of claim 1 in conjunction with its characterizing features. The following dependent claims give each advantageous embodiments of the invention. A motor vehicle drive train, in which a transmission according to the invention is used, is the subject matter of claim 15.

According to the invention, a transmission comprises a transmission input and a transmission output, and a first, a second, a third, a fourth and a fifth planetary gear set. The planetary gear sets each comprise a plurality of elements and serve to guide a flow of power from the transmission input to the transmission output. Further, six switching elements are provided, through the selective actuation of different power flow guides on the planetary gear trains under different gear ratios between the transmission input and transmission output can be displayed.

For the purposes of the invention, the transmission input is preferably formed at one end of a drive shaft, via which a drive movement is introduced into the transmission. The transmission output can be defined within the scope of the invention at the end of an output shaft, via which the drive gear ratio translated in accordance with the respectively shifted gear is led out of the transmission. The transmission output can also be formed by the toothing of a gear on which the translated drive movement can be tapped. Preferably, the transmission input and the transmission output are provided axially on mutually opposite ends of the transmission.

In the context of the invention, a "shaft" is understood to mean a rotatable component of the transmission via which each associated components of the transmission are connected to one another in an axially and / or rotationally fixed manner or via which such a connection can be produced upon actuation of a corresponding switching element. Thus, the respective shaft can also be present as an intermediate piece, via which a respective component is connected, for example, radially to the transmission output.

By "axial" in the context of the invention, an orientation in the direction of a transmission input axis is meant, along which the planetary gear sets are arranged coaxially to each other. The term "radial" is understood to mean an orientation in the diameter direction of a shaft lying on the transmission input axis.

The planetary gear sets are preferably arranged in the axial direction in the order of the first planetary gearset, the second planetary gearset, the third planetary gearset, the fourth planetary gearset, and the fifth planetary gearset. In principle, however, another arrangement could also be made within the scope of the invention.

The invention now includes the technical teaching that the third element of the second planetary gear set and the second element of the third planetary gear set are rotatably connected to each other and together via the first switching element a rotationally fixed component can be fixed, to which also the first element of the fourth planetary gear set by means of the second switching element can be fixed. Furthermore, the transmission input is non-rotatably connected to the first element of the second planetary gear set, whose second element is non-rotatably in communication with the third element of the fourth planetary gear set. The second element of the fourth planetary gearset, however, is rotatably connected to the transmission output and can be rotatably connected via the third switching element with the second element of the fifth planetary gear in conjunction, which is further rotatably connected by means of the fourth switching element with the first element of the fourth planetary gear set. Furthermore, the first element of the third planetary gear set is non-rotatably connected to the third element of the fifth planetary gear set in connection, the first element is permanently fixed to a rotationally fixed component. The third element of the third planetary gear set can be rotatably connected via the fifth switching element with the second element of the second planetary gear set and the third element of the fourth planetary gear set. Finally, in the first planetary gear set, a first coupling of the first element of the first planetary gear set with a rotationally fixed component, a second coupling of the second element of the first planetary gear set with the transmission input, and a third coupling of the third element of the first planetary gear set with the third element of the third planetary gear set , wherein of these couplings two couplings present as permanent non-rotatable connections, while in the remaining coupling a rotationally fixed connection by means of the sixth switching element can be produced.

In other words, in the transmission according to the invention, therefore, the third element of the second planetary gear set and the second element of the third planetary gear permanently connected to each other, while also between the second element of the second planetary gear set and the third element of the fourth planetary gear set a permanent rotationally fixed connection. Likewise, the first element of the third planetary gear and the third element of the fifth planetary gear set are permanently connected to each other rotationally fixed, whereas the first element of the fifth planetary gear set is permanently fixed to a non-rotatable component. The transmission input is also permanently non-rotatably in connection with the first element of the second planetary gear set, while the second element of the fourth planetary gear set and the transmission output are permanently connected to each other in a rotationally fixed manner.

By actuating the first switching element, the third element of the second planetary gear set and the second element of the third planetary gear set are fixed together on a non-rotatable component, to which also the first element of the fourth planetary gear set can be stopped by closing the second switching element. The rotationally fixed component of the second switching element can also be designed separately. The closing of the third switching element has a rotationally fixed connection of the second element of the fifth planetary gear set with the second element of the fourth planetary gear set and thus also the transmission output result. In addition, the second element of the fifth planetary gear set can be non-rotatably connected by pressing the fourth switching element with the first element of the fourth planetary gear set. The fifth switching element connects in the closed state, the second element of the second planetary gear set and the third element of the fourth planetary gear set together with the third element of the third planetary gear set.

In the case of the first planetary gear set there are three couplings of the elements of the first planetary gear set in the transmission according to the invention. Thus, a first coupling in the form of the first element of the first planetary gear set with a non-rotatable component is present, while in the case of the second element of the first planetary gear set, there is a second coupling to the transmission input. A third coupling is then present in the form of the third element of the first planetary gear set with the third element of the third planetary gear set. Two of the three aforementioned couplings are realized as permanent non-rotatable connections, while the remaining coupling is present as a compound that is made non-rotatably only by closing the sixth switching element.

For the purposes of the invention, a "coupling" is to be understood as meaning a connection which either consists of a permanently non-rotatable connection or is made non-rotatable only by actuating a respective switching element.

The non-rotatable components of the transmission according to the invention are permanently stationary components of the transmission, preferably a transmission housing or a part of such a transmission housing or components which are firmly connected to the transmission housing. The first element of the fifth planetary gear set is rotatably connected to a non-rotatable component and therefore stands permanently still. Similarly, third element of the second planetary gear set and the second element of the third planetary gear set together, as well as the first element of the fourth planetary gear set can be stopped alone by operating the respective associated switching element.

In the case of the invention, the first and second shifting elements are designed as brakes which, when activated, brake the respective rotatable component or the rotationally fixed components of the transmission which are connected to one another to a standstill and fix it on a non-rotatable component. In contrast, the third, the fourth and the fifth switching element are in the form of clutches which, when actuated, in each case match the respective associated rotatable components of the transmission in their rotational movements and subsequently connect them to one another in a torque-proof manner. Depending on which of the couplings of the first planetary gear set a rotationally fixed connection is made via the sixth switching element, it is at the sixth switching element to a brake or a clutch.

Preferably, the first switching element is provided axially between the third planetary gear set and the fourth planetary gear set, while the second switching element is placed in particular on a side facing away from the transmission input and the transmission output facing side of the fifth planetary gear set. Furthermore, the third shifting element and the fourth shifting element are preferably jointly provided axially between the fourth planetary gearset and the fifth planetary gearset and are furthermore preferably located axially next to one another. In addition, the third and the fourth switching element are in this case provided substantially at the same radial height. Due to the spatial arrangement of the third and the fourth switching element is a common supply of these two switching elements in question. The fifth switching element is axially preferably between the first planetary gear set and the second planetary gear set.

A respective rotationally fixed connection of the rotatable elements of the planetary gear sets according to the invention preferably realized via one or more intermediate waves, which may be present in a spatially dense position of the element as a short axial and / or radial spacers. Specifically, the permanently non-rotatably interconnected elements of the planetary gear sets can each be present either as non-rotatably interconnected individual components or in one piece. In the second-mentioned case, the respective elements and the optionally existing shaft are then formed by a common component, wherein this is realized in particular just when the respective elements in the transmission are spatially close to each other.

In the case of elements of the planetary gear sets, which are connected to one another in a rotationally fixed manner only by actuation of a respective switching element, a connection via one or even several intermediate shafts is likewise realized.

Overall, an inventive transmission is characterized by a compact design, low component loads, good gear efficiency and low transmission losses.

According to one embodiment of the invention, the second element of the first planetary gear rotatably connected to the transmission input and the third element of the first planetary gear rotatably connected to the third element of the third planetary gear in conjunction, while the first element of the first planetary gear set by means of the sixth switching element to a non-rotatable component can be.

In this case, therefore, the second element of the first planetary gear set permanently rotatably connected to the transmission input and the third element of the first planetary gear rotatably connected to the third element of the third planetary gear, whereas the first element of the first planetary gear set by pressing the sixth switching element on a non-rotatable component is fixed. In this case, the sixth switching element is preferably located axially on a side of the first planetary gear set that is adjacent to the transmission input.

According to an alternative embodiment possibility of the invention, the first element of the first planetary gearset is fixed to a non-rotatable component, while the third element of the first planetary gear set rotatably connected to the third element of the third planetary gear in combination. In contrast, the second element of the first planetary gear set can be rotatably connected to the transmission input by means of the sixth switching element.

In this variant, therefore, the first element of the first planetary gear set is permanently fixed to a rotationally fixed component, whereas the third element of the first planetary gear set is permanently non-rotatably connected to the third element of the third planetary gear set. By closing the sixth switching element, the second Element of the first planetary gear rotatably connected to the transmission input. In this case, the sixth switching element is axially preferably between the first planetary gear set and the second planetary gear set and is further preferably provided axially adjacent to the fifth switching element and radially inwardly thereto.

According to a further alternative embodiment of the invention, the first element of the first planetary gear set is fixed to a non-rotatable component, while the second element of the first planetary gear set rotatably connected to the transmission input. In contrast, the third element of the first planetary gear set can be non-rotatably connected by means of the sixth switching element with the third element of the third planetary gear set.

In this case, therefore, the first element of the first planetary gear set is permanently fixed again to a rotationally fixed component and the second element of the first planetary gear constantly rotatably connected to the transmission input, whereas only by closing the sixth switching element, a rotationally fixed connection of the third element of the first planetary gear to the third Element of the third planetary gear set is made. In this case, the sixth shift element is axially preferably in the wheel plane of the first planetary gear set and is thus placed substantially at the same axial height as the first planetary gear set, as well as radially surrounding this.

In the aforementioned variants of a transmission according to the invention ten forward gears, and two reverse gears can be realized by selectively closing three switching elements. In this case, a first forward gear is switched by operating the first, the fourth and the fifth shift element, while a second forward gear is formed by closing the first, the second and the fifth shift element. Alternatively, however, a second forward gear may also be represented by closing the first, second and sixth shifting elements or by operating the first, second and third shifting elements or by actuating the first, second and fourth shifting elements. Furthermore, a third forward speed results by actuating the second, the fourth and the fifth shifting element, whereas a fourth forward speed is switchable by actuating the second, the fourth and the sixth shifting element. Further, a fifth forward speed can be represented by closing the second, the third and the sixth shifting element, wherein for the shifting of a sixth forward speed, the second, the fifth and the sixth shifting element are to be actuated. On the other hand, a seventh forward speed is obtained by operating the third, fifth and sixth shift elements, while an eighth forward speed is switchable by operating the fourth, fifth and sixth shift elements. A ninth forward speed can be switched by operating the third, fourth and sixth shifting elements, while for the tenth forward speed shifting, the third, fourth and fifth shifting elements are to be closed.

A first reverse gear is obtained by operating the first, fourth and sixth shift elements, whereas a second reverse gear is engaged by closing the first, third and fifth shift elements.

With a suitable choice of stationary gear ratios of the planetary gear sets this is a suitable for the application in the field of a motor vehicle translation series realized. For a sequential shift of the forward gears according to their order is always the state of two switching elements to vary by one of the switching elements involved in the previous forward gear to open and another switching element to represent the subsequent forward gear is close. This then has the consequence that a shift between the courses can proceed very quickly.

Advantageously, in the transmission according to the invention, a reverse gear for a drive via the drive motor upstream of the transmission can be realized. This can be realized as an alternative or in addition to an arrangement of an electric machine in the transmission, in order to be able to realize a reverse drive of the motor vehicle in case of failure of the electric machine.

In a further development of the invention, a first additional gear by operating the first, the third and the sixth switching element, a second additional gear by operating the first, third and fourth switching element, and a third additional gear by operating the second, third and fifth switching element be switched. These additional gears can be represented in the individual aforementioned variants of a transmission according to the invention.

It is a further embodiment of the invention that the respective planetary gear is present as a minus planetary gear, wherein it is at the respective first element of each planetary gear to a respective sun gear at the respective second element of the respective planetary gear around a respective planet web and at the respective third element of the respective planetary gear set is a respective ring gear. A minus planetary set is composed in a manner known in principle to the person skilled in the art from the elements sun gear, planet carrier and ring gear, wherein the planet carrier carries at least one but preferably a plurality of planetary gears which in each case mesh with both the sun gear and the surrounding ring gear , Of the five planetary gear sets then one or more planetary gear sets are designed as such minus planetary gear sets. Particularly preferably, however, all planetary gear sets are in the form of minus planetary gear sets. whereby a particularly compact structure can be realized.

Alternatively or in addition thereto, the respective planetary gear set is in the form of a positive planetary gear set, wherein the respective first element of the respective planetary gear set is a respective sun gear, the respective second element of the respective planetary gear set is a respective ring gear and the respective third element of the respective planetary gear set is about a respective planetary land. In a plus-planetary gear set the elements sun gear, ring gear and planetary gear are also present, the latter at least one pair of planetary leads, in which one planetary gear with the inner sun gear and the other planet gear meshing with the surrounding ring gear, and the planet gears mesh with each other. In the transmission according to the invention, one or more planetary gear sets may be designed as such plus planetary gear sets.

Where there is a connection of the individual elements, a minus planetary gear set can be converted into a plus-planetary gear set, then compared to the execution as a minus planetary gear set the Hohlrad- and the Planetensteganbindung to exchange each other, and a respective Getriebestandübersetzung is to increase by one , Conversely, a plus planetary gear set could be replaced by a minus planetary gear set, if the connection of the elements of the transmission makes this possible. In this case, compared to the plus planetary gear set, the ring gear and the planet web connection would then also have to be exchanged with each other, as well as a respective gearbox ratio reduced by one. As already mentioned, but preferably all planetary gear sets are designed as minus planetary gear sets.

According to a further embodiment of the invention, one or more switching elements are each realized as non-positive switching elements. Non-positive switching elements have the advantage that they can be switched under load, so that a change between the courses without interruption of traction is enforceable. But particularly preferably, the first switching element is designed as a form-locking switching element, such as a dog clutch or lock synchronization. For the first switching element is involved in the representation of the first two forward gears and the two reverse gears, so that a closing in style of the motor vehicle is here to make. A form-fitting switching element has the advantage over a non-positive switching element that only slight drag torques occur in the opened state, so that a higher efficiency can be realized.

In a further development of the invention, the transmission input is rotatably coupled to a power take-off. In this case, the transmission according to the invention is thus equipped with a power take-off, via which a drive of ancillary units or the like can take place. The power take-off can be connected directly to the transmission input of the transmission, but the power take-off preferably connects non-rotatably to the second element of the first planetary gear set. More preferably, the power take-off is axially between the first planetary gear set and the transmission input.

According to a further embodiment of the invention, the transmission input is formed on a drive shaft and the transmission output on an output shaft, wherein the drive shaft and the output shaft are coaxial with each other. Here, the transmission input is preferably provided at an axial end of the transmission, while the transmission output is configured axially at an opposite end of the transmission. This type of arrangement is particularly suitable for use in a motor vehicle with an aligned in the direction of travel of the motor vehicle drive train. Alternatively, the transmission output can also be aligned transversely to the transmission input in order to realize a structure which is suitable for a transversely oriented to the direction of travel of the motor vehicle drive train. In this case, the transmission output may be formed by a toothing which meshes with a toothing of a transmission axis arranged parallel to the axis of the shaft. The axle differential of a drive axle can then be arranged on this shaft.

In a further development of the invention, an electric machine is provided whose rotor is rotatably coupled to one of the rotatable components of the transmission. Preferably, a stator of the electric machine is then non-rotatably connected to a non-rotatable component of the transmission, wherein the electric machine in this case can be operated by electric motor and / or generator to realize different functions. In particular, a purely electric driving, a boosting via the electric machine, a deceleration and recuperation and / or a synchronization in the transmission via the electric machine can be performed. The rotor of the electric machine can be coaxial with the respective component or be arranged off-axis to this, then in the latter case, a coupling via one or more intermediate gear ratios, for example in the form of spur gears, or a traction drive, such as a chain drive, be realized can.

Preferably, however, the rotor of the electric machine is rotatably coupled to the transmission input, thereby a purely electric driving the Motor vehicle is displayed in a suitable manner. More preferably, one or more of the switching elements are used as internal starting elements for electric driving. Particularly suitable for this purpose are the first switching element, the fourth switching element or the fifth switching element, since these are each closed both in one of the reverse gears, as well as in the first forward gear. As a further alternative, however, a separate starting clutch can be used, which is positioned between the electric machine and the gear set.

For purely electric driving one of the gears is engaged in the transmission, wherein in the forward gears while a reverse drive of the motor vehicle is realized by an opposite rotational movement is initiated via the electric machine, whereby the reverse movement of the motor vehicle takes place in the ratio of the respective forward gear. As a result, the gear ratios of the forward gears can be used for both the electric forward and the reverse electric drive. The rotor of the electric machine could be apart from the transmission input also connected to one of the other, rotatable components of the transmission.

According to a further embodiment of the invention, which is realized in particular in combination with the aforementioned arrangement of an electric machine, a separating clutch is also provided, via which the transmission input to a connecting shaft is rotatably connected. The connecting shaft then serves within a motor vehicle drive train of the connection to the drive machine. The provision of the separating clutch has the advantage that in the course of purely electric driving a connection to the drive machine can be interrupted, so that they are not dragged. The separating clutch is preferably designed as a non-positive switching element, such as a multi-disc clutch, but may also be present as a positive switching element, such as a dog clutch or lock synchronization.

In general, the transmission can in principle be preceded by a starting element, for example a hydrodynamic torque converter or a friction clutch. This starting element can then also be part of the transmission and serves to design a start-up process by allowing a slip speed between the internal combustion engine and the transmission input of the transmission. In this case, one of the switching elements of the transmission or the possibly existing separating clutch can be designed as such a starting element by being present as a friction switching element. In addition, a freewheel to the transmission housing or to another shaft can in principle be arranged on each shaft of the transmission.

The transmission according to the invention is in particular part of a motor vehicle drive train and is then arranged between a drive motor of the motor vehicle designed in particular as an internal combustion engine and further components of the drive train following in the direction of power flow to drive wheels of the motor vehicle. Here, the transmission input of the transmission is either permanently non-rotatably coupled to a crankshaft of the internal combustion engine or connected via an intermediate disconnect clutch or a starting element with this, between the engine and transmission also a torsional vibration damper can be provided. On the output side, the transmission within the motor vehicle drive train is then preferably coupled to an axle drive of a drive axle of the motor vehicle, although here also a connection to a longitudinal differential may be present, via which a distribution takes place on a plurality of driven axles of the motor vehicle. The axle or the longitudinal differential can be arranged with the transmission in a common housing. Likewise, a torsional vibration damper can also be integrated into this housing.

The fact that two components of the transmission are non-rotatably "connected" or "coupled" or "communicate with one another" means in the sense of the invention a permanent connection of these components, so that they can not rotate independently of one another. In this respect, no switching element is provided between these components, in which it may be elements of the planetary gear sets or shafts or a non-rotatable component of the transmission, but the corresponding components are rigidly coupled together.

However, if a switching element is provided between two components of the transmission, then these components are not permanently rotatably coupled to each other, but a rotationally fixed coupling is made only by pressing the intermediate switching element. In this case, an actuation of the switching element in the sense of the invention means that the relevant switching element is transferred into a closed state and, as a result, the components directly coupled to it in their rotational movements equal to one another. In the case of an embodiment of the relevant switching element as a form-locking switching element on this directly rotatably connected to each other components are running at the same speed, while in the case of a non-positive switching element and after a Actuate desselbigen speed differences between the components can exist. This intentional or unwanted state is still referred to in the context of the invention as a rotationally fixed connection of the respective components via the switching element.

The invention is not limited to the specified combination of the features of the main claim or the claims dependent thereon. It also results in ways to combine individual features, even if they emerge from the claims, the following description of preferred embodiments of the invention or directly from the drawings. The reference of the claims to the drawings by use of reference numerals is not intended to limit the scope of the claims.

• 1 eine schematische Ansicht eines Kraftfahrzeugantriebsstranges, in welchem ein erfindungsgemäßes Getriebe zur Anwendung kommt;
• 2 eine schematische Ansicht eines Getriebes entsprechend einer ersten Ausführungsform der Erfindung;
• 3 eine schematische Darstellung eines Getriebes gemäß einer zweiten Ausgestaltungsmöglichkeit der Erfindung;
• 4 eine schematische Ansicht eines Getriebes entsprechend einer dritten Ausführungsform der Erfindung;
• 5 eine schematische Darstellung eines Getriebes gemäß einer vierten Ausgestaltungsmöglichkeit der Erfindung;
• 6 eine schematische Ansicht eines Getriebes entsprechend einer fünften Ausführungsform der Erfindung; und
• 7 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 6.

Advantageous embodiments of the invention, which are explained below, are shown in the drawings. It shows:

• 1 a schematic view of a motor vehicle drive train, in which a transmission according to the invention is used;
• 2 a schematic view of a transmission according to a first embodiment of the invention;
• 3 a schematic representation of a transmission according to a second embodiment of the invention;
• 4 a schematic view of a transmission according to a third embodiment of the invention;
• 5 a schematic representation of a transmission according to a fourth embodiment of the invention;
• 6 a schematic view of a transmission according to a fifth embodiment of the invention; and
• 7 an exemplary circuit diagram of the transmission of the 2 to 6 ,

1 shows a schematic view of a motor vehicle drive train, in which an internal combustion engine VKM via an intermediate torsional vibration damper TS with a gear G connected is. The transmission G on the output side is an axle drive AG downstream, via which a drive power on drive wheels DW a drive axle of the motor vehicle is distributed. The gear G and the axle drive AG can be summarized in a common transmission housing, in which then also the torsional vibration damper TS can be integrated. As well as in 1 it can be seen, are the internal combustion engine VKM , the torsional vibration damper TS , The gear G and also the axle drive AG aligned in the direction of travel of the motor vehicle.

Out 2 is a schematic representation of the transmission G according to a first embodiment of the invention. As can be seen, the transmission includes G a first planetary gear set P1 , a second planetary gear set P2 , a third planetary gear set P3 , a fourth planetary gear set P4 and a fifth planetary gear set P5. Each of the planetary gear sets P1 . P2 . P3 . P4 and P5 each has a first element E11 respectively. E12 respectively. E13 respectively. E14 respectively. E15 , a second element each E21 respectively. E22 respectively. E23 respectively. E24 respectively. E25 and a third element each E31 respectively. E32 respectively. E33 respectively. E34 respectively. E35 on. The respective first element E11 respectively. E12 respectively. E13 respectively. E14 respectively. E15 is always by a sun gear of the respective planetary gear set P1 respectively. P2 respectively. P3 respectively. P4 respectively. P5 formed while the respective second element E21 respectively. E22 respectively. E23 respectively. E24 respectively. E25 at the planetary gear sets P1 . P2 . P3 . P4 and P5 each as a planetary bridge is present. The remaining third element E31 respectively. E32 respectively. E33 respectively. E34 respectively. E35 is then by a respective ring gear of the respective planetary gear set P1 respectively. P2 respectively. P3 respectively. P4 respectively. P5 educated.

The planetary gear sets P1 . P2 . P3 . P4 and P5 In the present case, these are each designed as negative planetary gear sets, in which the respective planetary web, but preferably a plurality of planet gears rotatably mounted, which are in mesh with the radially inner sun gear and also with the surrounding ring gear in detail.

Where it allows the connection, but one or more of the planetary gear sets P1 . P2 . P3 . P4 and P5 be executed as plus planetary gear sets. In the case of a plus planetary gear set, the planet carrier then carries at least one pair of planetary gears, whose planet gears mesh with the radially inner sun gear and a planetary gear with the radially surrounding ring gear, and the planetary gears of the pair of wheels intermesh with one another. In comparison to a respective version as a minus planetary gear set would then for the transfer to a plus-planetary gear set the respective second element E21 respectively. E22 respectively. E23 respectively. E24 respectively. E25 through the respective ring gear and the respective third element E31 respectively. E32 respectively. E33 respectively. E34 respectively. E35 formed by the respective planet web and also a respective transmission gear ratio can be increased by one.

In the present case are the first planetary gear set P1 , the second planetary gear set P2 , the third planetary gear P3 , the fourth planetary gear set P4 and the fifth planetary gear set P5 axially in the order of the first planetary gear set P1 , second planetary gear set P2 , third planetary gear set P3 , fourth planetary gear set P4 and fifth planetary gear set P5 between a transmission input Level 1-A and a transmission output GW2 -A arranged.

The transmission input Level 1-A and the transmission output GW2-A are coaxial with each other at opposite axial ends of the transmission G intended. The transmission input is used Level 1-A in the motor vehicle drive train 1 a connection to the internal combustion engine VKM while the gearbox G at the transmission output GW2-A with the following axle drive AG connected is.

As in 2 can be seen, includes the gearbox G a total of six switching elements in the form of a first switching element B1 , a second switching element B2 , a third switching element K1 , a fourth switching element K2 , a fifth switching element K3 and a sixth switching element B3 , Here are the switching elements B1 . B2 . K1 . K2 . K3 and B3 each designed as non-positive switching elements and are preferably before as lamella switching elements. In addition, the third switching element K1 , the fourth switching element K2 and the fifth switching element K3 designed here as couplings, while the first switching element B1 , the second switching element B2 and the sixth switching element B3 as brakes.

In the present case are the second element E21 of the first planetary gear set P1 and the first element E12 of the second planetary gear set P2 rotatably connected to each other and are rotatably together with a drive shaft LV1 in communication with the transmission input at one axial end Level 1-A Are defined. The third element E31 of the first planetary gear set P1 is against rotation with the third element E33 of the third planetary gear set P3 connected, its second element E23 non-rotatable with the third element E32 of the second planetary gear set P2 is in communication and together with this by means of the first switching element B1 on a non-rotatable component GG can be fixed. In the non-rotatable components GG this is preferably a transmission housing of the transmission G or a part of such a transmission housing.

Furthermore, the first element E13 of the third planetary gear set rotatably with the third element E35 of the fifth planetary gear set P5 connected, wherein the first element E15 of the fifth planetary gear set P5 permanently on a non-rotatable component GG is fixed. On the non-rotatable component GG can also be the first element E14 of the fourth planetary gear set P4 by closing the second switching element B2 be set, the first element E14 of the fourth planetary gear set P4 further by actuating the fourth switching element K2 rotatably with the second element E25 of the fifth planetary gear set P5 can be connected.

Apart from the rotationally fixed connectivity to the first element E14 of the fourth planetary gear set P4 can the second element E25 of the fifth planetary gear set P5 also by means of the third switching element K1 rotatably with the second element E24 of the fourth planetary gear set P4 be associated, which permanently rotatably with an output shaft GW2 connected is. The output shaft GW2 forms at one to the transmission input Level 1-A opposite axial end of the transmission G the transmission output GW2-A out. A closing of the third switching element K1 has accordingly also a rotationally fixed connection of the second element E25 of the fifth planetary gear set P5 with the output shaft GW2 result.

Further, the third element is E34 of the fourth planetary gear set P4 permanently rotationally fixed with the second element E22 of the second planetary gear set P2 connected and may together with this by closing the fifth switching element K3 non-rotatable with the third element E31 of the first planetary gear set P1 and the third element E33 of the third planetary gear set P3 get connected. Finally, there may be the first element E11 of the first planetary gear set P1 via the sixth switching element B3 on a non-rotatable component GG be fixed.

The first switching element B1 lies axially between the third planetary gear P3 and the fourth planetary gear set P4 while the second switching element B2 axially on a transmission output GW2-A facing side of the fifth planetary gear set P5 is provided.

As well as in 2 can be seen, are the third switching element K1 and the fourth switching element K2 together axially between the fourth planetary gear P4 and the fifth planetary gear set P5 placed and lie axially directly next to each other. In addition, the third switching element K1 and the fourth switching element K2 arranged radially substantially at the same height. Due to the spatial arrangement of the third switching element K1 and the fourth switching element K2 comes with the gearbox G Therefore, a common supply of the two switching elements K1 and K2 in question via a common supply line.

The fifth switching element K3 is axially between the first planetary gear set P1 and the second planetary gear set P2 provided, whereas the sixth switching element B3 axially on a transmission input Level 1-A facing side of the first planetary gear set P1 is arranged.

In addition, goes out 3 a schematic representation of a transmission G according to a second embodiment of the invention, which in this case essentially according to the previous variant 2 equivalent. The only difference is that in addition a power take-off PTO is provided, which rotatably with the transmission input Level 1-A connected is. Specifically, the power take-off PTO rotationally fixed to the second element E21 of the first planetary gear set P1 connected, which is so rotatably with the drive shaft LV1 and thus also the transmission input Level 1-A communicates. Otherwise, the embodiment corresponds to 3 the previous variant 2 so that reference is made to what has been described.

4 shows a schematic view of a transmission G according to a third embodiment of the invention. Again, this design option corresponds again largely to the variant 2 , in contrast to the first element E11 of the first planetary gear set B1 permanently on a non-rotatable component GG is fixed, whereas a rotationally fixed connection between the second element E21 of the first planetary gear set P1 and the drive shaft LV1 only by closing a sixth switching element K4 will be produced. The sixth switching element K4 is axially between the first planetary gear P1 and the second planetary gear set P2 provided and is axially adjacent to the fifth switching element K3 , In addition, the sixth switching element K4 while radially inward to the fifth switching element K3 placed, due to the spatial arrangement of the switching elements K3 and K4 Here, too, if necessary, a joint supply would be conceivable. Otherwise, the design option corresponds to 4 according to the variant 2 so that reference is made to what has been described.

Furthermore goes out 5 a schematic representation of a transmission G according to a fourth embodiment of the invention, which in turn largely the possibility of design according to 2 equivalent. It is different, however, that the first element E11 of the first planetary gear set P1 permanently on a non-rotatable component GG is fixed, whereas a rotationally fixed connection of the third element P31 of the first planetary gear set P1 with the third element E33 of the third planetary gear set P3 only in the closed state of a sixth switching element K4 is made. This sixth switching element K4 is axially in the gear plane of the first planetary gear set P1 and radially surrounding it. Due to the spatial arrangement in the vicinity of the fifth switching element K3 may be a common supply of the fifth switching element K3 and the sixth switching element K4 be realized. Otherwise, the embodiment corresponds to 5 according to the variant 2 so that reference is made to what has been described.

Finally shows 6 a schematic representation of a transmission G according to a fifth embodiment of the invention. This embodiment also essentially corresponds to the variant 2 , in contrast, in addition to an electric machine EM is provided, whose stator S on a non-rotatable component GG is fixed while a rotor R the electric machine EM rotatably with the drive shaft LV1 connected is. Furthermore, the drive shaft LV1 at the transmission input Level 1-A via an intermediate separating clutch K0 , which is designed here as a lamellae switching element, with a connecting shaft AT rotatably connected, which in turn connected to a crankshaft of the internal combustion engine VKM by means of the intermediate torsional vibration damper TS connected is. Due to the rotationally fixed connection of the rotor R with the drive shaft LV1 is the electric machine EM coaxial with the drive shaft LV1 placed.

About the electric machine EM In this case, a purely electric driving can be realized, in which case the separating clutch K0 is opened to the transmission input Level 1-A from the connection shaft AT to decouple and the internal combustion engine VKM not to lug. Otherwise, the embodiment corresponds to 6 according to the variant 2 so that reference is made to what has been described.

In 7 is an exemplary circuit diagram for the transmission G from the 2 to 6 tabulated. As can be seen, in each case a total of ten forward gears 1 to 10 , as well as two reverse gears R1 and R2 be realized, which is marked in the columns of the circuit diagram with an X respectively, which of the switching elements B1 . B2 . K1 . K2 . K3 and B3 respectively. K4 in which of the forward gears 1 to 10 and the reverse gears R1 and R2 each is closed. In each of the forward gears 1 to 10 and the reverse gears R1 and R2 are each three of the switching elements B1 . B2 . K1 . K2 . K3 and B3 respectively. K4 closed, with a successive circuit of the forward gears 1 to 10 , with the exception of variants 2.2 and 2.3 a second forward gear, one of the involved switching elements to open and close another switching element in the following.

As in 7 can be seen, is a first forward gear 1 by actuating the first switching element B1 , the fourth switching element K2 and the fifth switching element K3 switched, starting from this, a second forward gear 2.1 is formed by the fourth switching element K2 opened and in the following the second switching element B2 is closed. Alternatively, in a second forward gear 2.2 be switched by both the fourth switching element K2 , as well as the fifth switching element K3 opened and the second switching element B2 and the sixth switching element B3 respectively. K4 getting closed. Next alternatively, a second forward gear 2.3 by opening the fourth switching element K2 and the fifth switching element K3 and closing the second switching element B2 and the third switching element K1 be formed. Likewise, there is a second forward gear 2.4 starting from the first forward gear 1 by opening the fifth switching element K3 and closing the second switching element B2 , The forward gears 2.1 and 2.4 are preferred in this case, since in this case only the switching state of two switching elements with respect to the first forward gear 1 to change.

Furthermore, a third forward gear 3 switched by the second switching element B2 , the fourth switching element K2 and the fifth switching element K3 getting closed. Based on this results then a fourth forward gear 4 by opening the fifth switching element K3 and closing the sixth switching element B3 respectively. K4 , This results in a fifth forward gear 5 by opening the fourth switching element K2 and actuating the third switching element K1 , starting from this in a sixth forward gear 6 is switched by the third switching element K1 opened and the fifth switching element K3 is closed. To shift to a seventh forward gear 7 is then the second switching element B2 to open and the third switching element K1 close.

Starting from the seventh forward gear 7 will then be in an eighth forward 8th switched by the third switching element K1 in an unactuated and the fourth switching element K2 is transferred to an actuated state. To further upshift into a ninth forward gear 9 is the fifth switching element below K3 to open and the third switching element K1 close. Finally, the ninth forward gear 9 in the tenth forward gear 10 switched by the sixth switching element B3 respectively. K4 in an unactuated state and then the fifth switching element K3 is transferred to an actuated state.

The first reverse R1 , in which a reverse drive of the motor vehicle even when driven by the internal combustion engine VKM can be realized, however, by closing the first switching element B1 , the fourth switching element K2 and the sixth switching element B3 respectively. K4 connected. In contrast, there is the second reverse gear R2 by actuating the first switching element B1 , the third switching element K1 and the fifth switching element K3 ,

In the transmissions go out of the 2 to 6 can also have additional aisles Z1 to Z3 are shown, which, however, not good in the translation series of the respective transmission G fit. This results in a first additional gear Z1 by closing the first switching element B1 , the third switching element K1 and the sixth switching element B3 respectively. K4 whereas a second additional gear Z2 by actuating the first switching element B1 , the third switching element K1 and the fourth switching element K2 is representable. Finally, a third additional gear Z3 by closing the second switching element B2 , the third switching element K1 and the fifth switching element K3 be switched.

As in the 2 to 6 is shown, is the first switching element B1 designed as non-positive switching element. However, the first switching element could B1 Also be realized as a form-locking switching element, such as locking synchronization or as a claw switching element.

Furthermore, the gears can also G according to the embodiments of 3 to 5 analogous to the variant according to 6 be hybridized. In addition, a power take-off PTO also analogous to the in 3 illustrated variant in the embodiments according to the 4 to 6 will be realized.

By means of the embodiments according to the invention, a transmission with a compact design and a good efficiency can be realized.

LIST OF REFERENCE NUMBERS

G

transmission

GG

Non-rotating component

P1

First planetary gear set

E11

First element of the first planetary gear set

E21

Second element of the first planetary gear set

E31

Third element of the first planetary gear set

P2

Second planetary gear set

E12

First element of the second planetary gear set

E22

Second element of the second planetary gear set

E32

Third element of the second planetary gear set

P3

Third planetary gear set

E13

First element of the third planetary gear set

E23

Second element of the third planetary gear set

E33

Third element of the third planetary gear set

P4

Fourth planetary gear set

E14

First element of the fourth planetary gear set

E24

Second element of the fourth planetary gear set

E34

Third element of the fourth planetary gear set

P5

Fifth planetary gear set

E15

First element of the fifth planetary gear set

E25

Second element of the fifth planetary gear set

E35

Third element of the fifth planetary gear set

B1

First switching element

B2

Second switching element

K1

Third switching element

K2

Fourth switching element

K3

Fifth switching element

B3

Sixth switching element

K4

Sixth switching element

1

First forward

2.1

Second forward speed

2.2

Second forward speed

2.3

Second forward speed

2.4

Second forward speed

3

Third forward

4

Fourth forward

5

Fifth forward speed

6

Sixth forward

7

Seventh forward

8th

Eighth forward

9

Ninth forward

10

Tenth forward

R1

First reverse

R2

Second reverse

Z1

First additional gear

Z2

Second additional gear

Z3

Third additional gear

LV1

drive shaft

Level 1-A

transmission input

GW2

output shaft

GW2-A

transmission output

PTO

PTO

EM

electric machine

S

stator

R

rotor

AT

connecting shaft

K0

separating clutch

VKM

Internal combustion engine

TS

torsional vibration damper

AG

transaxles

DW

drive wheels

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• KR 20160072696A [0003]

Claims (15)

Transmission (G) for a motor vehicle, comprising a transmission input (GW1-A) and a transmission output (GW2-A), and a first (P1), a second (P2), a third (P3), a fourth (P4) and a fifth planetary gear set (P5), wherein the planetary gear sets (P1, P2, P3, P4, P5) each have a plurality of elements (E11, E12, E13, E21, E22, E23, E31, E32, E33, E14, E24, E34, E15 , E25, E35), wherein a first (B1), a second (B2), a third (K1), a fourth (K2), a fifth (K3) and a sixth switching element (B3; K4) are provided the selective actuation of different force flow guides through planetary gear sets (P1, P2, P3, P4, P5) with circuit of different programs (1 to 10, R1 and R2) between the transmission input (GW1-A) and transmission output (GW2-A) can be displayed, characterized characterized in that - the third element (E32) of the second planetary gear set (P2) and the second element (E23) of the third planetary gear set (P3) rotatably connected to each other u nd together on the first switching element (B1) on a non-rotatable component (GG) can be fixed, - wherein the first element (E14) of the fourth planetary gear set (P4) by means of the second switching element (B2) also on a non-rotatable member (GG) can be fixed in that the transmission input (GW1-A) is non-rotatably connected to the first element (E12) of the second planetary gear set (P2) whose second element (E22) is non-rotatably connected to the third element (E34) of the fourth planetary gear set (P4) in that the second element (E24) of the fourth planetary gear set (P4) is connected in a rotationally fixed manner to the transmission output (GW2-A) and via the third switching element (K1) in a rotationally fixed manner to the second element (E25) of the fifth planetary gear set (P5) can be brought, which by means of the fourth switching element (K2) rotatably connected to the first element (E14) of the fourth planetary gear set (P4) is connectable, - that the first element (E13) of the third planetary gear set (P3) rotatably is in communication with the third element (E35) of the fifth planetary gear set (P5) whose first element (E15) is permanently fixed to a non-rotatable component (GG), - that the third element (E33) of the third planetary gear set (P3) via the fifth switching element (K3) rotationally fixed to the second element (E22) of the second planetary gear set (P2) and the third element (E34) of the fourth planetary gear set (P4) is connectable, - and that in the first planetary gear set (P1) a first coupling of the first element (E11) of the first planetary gear set (P1) with a non-rotatable component (GG), a second coupling of the second element (E21) of the first planetary gear set (P1) with the transmission input (GW1-A), and a third coupling of the third element (E31 ) of the first planetary gear set (P1) with the third element (E33) of the third planetary gear set (P3), of these couplings two couplings present as permanent non-rotatable connections, while in the still verb Pairing coupling a rotationally fixed connection by means of the sixth switching element (B3; K4) can be produced. Transmission (G) to Claim 1 , characterized in that the second element (E21) of the first planetary gear set (P1) rotationally fixed to the transmission input (GW1-A) and the third element (E31) of the first planetary gear set (P1) rotationally fixed to the third element (E33) of the third planetary gear set (P3) is in communication, while the first element (E11) of the first planetary gear set (P1) by means of the sixth switching element (B3) on a rotationally fixed component (GG) can be fixed. Transmission (G) to Claim 1 , characterized in that the first element (E11) of the first planetary gear set (P1) is fixed to a non-rotatable component (GG) and the third element (E31) of the first planetary gear set (P1) rotationally fixed to the third element (E33) of the third planetary gear set (P3) is in communication, while the second element (E21) of the first planetary gear set (P1) by means of the sixth switching element (K4) rotatably connected to the transmission input (GW1-A) is connectable. Transmission (G) to Claim 1 , characterized in that the first element (E11) of the first planetary gear set (P1) is fixed to a non-rotatable component (GG) and the second element (E21) of the first planetary gear set (P1) rotatably connected to the transmission input (GW1-A) in combination stands, while the third element (E31) of the first planetary gear set (P1) by means of the sixth switching element (K4) rotatably connected to the third element (E33) of the third planetary gear set (P3) is connectable. Transmission (G) according to one of Claims 1 to 4 , characterized in that a first forward gear (1) by operating the first (B1), the fourth (K2) and the fifth switching element (K3), a second forward gear (2.1) by operating the first (B1), the second (B2 ) and the fifth switching element (K3) or (2.2) by actuating the first (B1), the second (B2) and the sixth switching element (B3 or K4) or (2.3) by operating the first (B1), the second (B2) and the third switching element (K1) or (2.4) by operating the first (B1), the second (B2 ) and the fourth shift element (K2), a third forward gear (3) by operating the second (B2), the fourth (K2) and the fifth shift element (K3), a fourth forward gear (4) by operating the second (B2), a fifth forward gear (5) by actuating the second (B2), the third (K1) and the sixth shifting element (B3 or K4), a sixth forward gear (5) of the fourth (K2) and the sixth shifting element (B3 or K4) 6) by operating the second (B2), the fifth (K3) and the sixth switching element (B3 or K4), a seventh forward gear (7) by actuating the third (K1), the fifth (K3) and the sixth switching element ( B3 or K4), an eighth forward gear (8) by actuating the fourth (K2), the fifth (K3) and the sixth switching element (B3 or B3) K4), a ninth forward gear (9) by operating the third (K1), the fourth (K2) and the sixth shift element (B3 or K4), a tenth forward gear (10) by operating the third (K1), the fourth ( K2) and the fifth shift element (K3), a first reverse gear (R1) by operating the first (B1), the fourth (K2) and the sixth shift element (B3 or K4), and a second reverse gear (R2) by operating the first (B1), the third (K1) and the fifth switching element (K3) is switchable. Transmission (G) according to one of the preceding claims, characterized in that a first additional gear (Z1) by actuating the first (B1), the third (K1) and the sixth switching element (B3 or K4), a second additional gear (Z2) by actuating the first (B1), the third (K1) and the fourth switching element (K2), and a third additional gear (Z3) by operating the second (B2), the third (K1) and the fifth switching element (K3) is switchable , Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P1, P2, P3, P4, P5) is present as a minus planetary gear set, wherein it is at the respective first element (E11, E12, E13, E14 , E15) of the respective planetary gear set (P1, P2, P3, P4, P5) about a respective sun gear, at the respective second element (E21, E22, E23, E24, E25) of the respective planetary gear set (P1, P2, P3, P4, P5) around a respective planetary land and at the respective third element (E31, E32, E33, E34, E35) of the respective planetary gear set (P1, P2, P3, P4, P5) is a respective ring gear. Transmission according to one of the preceding claims, characterized in that the respective planetary gear set is present as a plus-planetary gear set, wherein it is at the respective first element of the respective planetary gear set to a respective sun gear, at the respective second element of the respective planetary gear set to a respective ring gear and at the respective third element of the respective planetary gear set is a respective planet web. Transmission (G) according to one of the preceding claims, characterized in that one or more switching elements (B1, B2, K1, K2, K3, B3, B1, B2, K1, K2, K3, K4) are each realized as non-positive switching element. Transmission according to one of the preceding claims, characterized in that the first switching element is realized as a positive switching element. Transmission (G) according to one of the preceding claims, characterized in that the transmission input (GW1-A) is rotatably coupled to a PTO (PTO). Transmission (G) according to one of the preceding claims, characterized in that the transmission input (GW1-A) on a drive shaft (GW1) and the transmission output (GW2-A) on an output shaft (GW2) is formed, wherein the drive shaft (GW1) and the output shaft (GW2) are coaxial with each other. Transmission (G) according to one of the preceding claims, characterized in that an electric machine (EM) is provided, whose rotor (R) is coupled to a rotatable component. Transmission (G) according to one of the preceding claims, characterized in that in addition a separating clutch (K0) is provided, via which the transmission input (GW1-A) with a connecting shaft (AN) is rotatably connected. Motor vehicle drive train, comprising a transmission (G) after one or more of the Claims 1 to 14 ,

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